Oil burner supply system



NOV. 15, 1932;v c RAYFlELD 1,888,015

OIL BURNER SUPPLY SYSTEM Filed Feb. 24, 1930 3 Sheets-Sheet l Czar/95LRag/field 3 Sheets-Sheet C. L. RAY'FIELD OIL BURNER SUPPLY SYSTEM Fk ledFeb. 24,- 1930 JHI w w w Nov. 15,

a. Bmmmw Nov. 15, 1932. c. 1.. RAYFIELD 1,883,015

011. BURNER SUPPLY SYSTEM Filed Feb. 24, 1930 3 Sheets-Sheet C PatentedNov. 15, 1932 UNITED PATENT OFFICE CHARLIE-L. RAYI'IELD, OF CHICAGO,ILLINOIS, ASSIGNOR TO RAYFIELD MFG. CO., OF

CHICAGO, ILLINOIS, A CORPORATION OF ILLINOIS k OIL BURNER SUPPLY SYSTEMY Application filed rebruarfu, 1930. Serial No. 430,574,

I This invention relates to oil burner supply systems and particularlyto improved pumping apparatus and arrangement for deliver mg accuratelyproportioned combustion mix-i ture to a heating device or furnace.

An important object of the invention is to utilize a pump structure ofthe angular rotary type providing two interconnected I pump legs orsections, and the selective utilization of pump plungers for pumping oiland air and forming the combustion mixture.

A further object of the invention is to utilize part of the plungers ofone pump section for pumping oil for the combustion mix-.

ture and to utilize the other plungers of such pump section and all theplungers of the other pump section for pumping air for-the combustionmixture. I

Another object is to provide an arrangement in which oil and air isdelivered in. measured quantities to the pump sections toproduce anaccurately proportioned combus-,

tion mixture.

A further obpect is to utilize some of the plungers'of one of the pumpsections for pumping metered oil and air for thecombustion mixture, andto utilize the other. plungers of such pump section and the plungers ofthe other pump section for respectively pumpinglindependent streams ofair supply for the combustion mixture.

Another important object is to utilize an auxiliary oil supply source inthe form of a vacuum tank and to utilize part of the pump structure forcreating vacuum in said tankto maintain the oil supply therein, and utiv,lizing another part of the ump structure for pumping oil from the tantogether with means for mixing the pumped oiland air to form thecombustion mixture.

v Still a further object of the invention is to utilize an intermediatesource of oil supply in the form of a vacuum tank; to utilize part ofthe plungers of one pump section for drawing air supply for thecombustion mixture from the vacuum tank tothereby create vacuum-in thetank to maintain the oil supply thereto from a main source, andtoutilizethe other plungers of such pump section for pumping oil fromthe vacuum tank for a rich properly and efiiciently proportionedcombustion mixture;

A further objectis to provide improved means and arrangement foraccurately metering oil and air supply to the pump structure.

- Still another object is to provide improved means for stabilizing thepressure and volume of the air and oil delivered by the pump structureto the burner nozzle or other sourceof consumption of the combustionmixture. A. further object is to interpose closed I pressure balancingand stabilizing chambers between the discharge ends of the air and oilstreams from the pump structure and the combustion mixture injectionnozzle or burner for the heating device to be served.

The above enumerated features and other features of the invention areincorporated in the structure disclosed on the drawings, in whichdrawings 1 Figure 1 is a side elevation of my improved compactlyarranged apparatus and circuits for supplying combustion mixture;

Figure 2 1s a plan view of the apparatus;

Figure 3 is a vertical diametral section of the angular pump structure;

Figure 4 is a section on line IVIV of F igure v Figure 5 is a section onplane VY of Figure 3;

Figure 6 is a plan view of the head of the vertical pump section onplane VIVI of Figure 4;

Figure 7 is a view of the inner side of the head of the horizontal pumpsection on'plane VIIVII of Figure 3;

Figure 8 is an enlarged sectional View I showing the pressurestabilizing chambers and a mam ejector or nozzle; and- Figure 9 is anenlarged vertical diametral section of the oil metering fitting on thevacuum tank.

The angular pump structure shown has the pump sections A and Bcomprising respectively the cylindrical housings 10 and 11 detachablysecured together at their inner ends along a. plane of by means of theflanges 12 and 13 and screws 14, the housings being thus at a rightangle with each other. A head 15 is applied to the outer end of thehousing 10 by means of screws 16, while a head 17 is detachably securedto the outer endof the housing 11 by screws 18.

At the juncture of the housings is the chamber 19. between which and thehead 15 of pump section A is the rotary cylinder 20 which is confinedaxially between the head and the annular shoulder or flange 21. Betweenthe chamber 19 and the head 17 of pump section B is the rotary cylinder22 which is axially confined between the head and the annular shoulder23.

The cylinder 20 has a plurality of bores 24 extending therethroughequidistant from its axis. Four such bores are shown regularly spacedaround the cylinder axis, and recipro-cable in each bore is a plunger25. The arrangement in cylinder 22 is the same as in cylinder 20, thebores 26a, 26b, 26c, and 26d having the pistons 27 reciprocable therein.The plungers of the corresponding bores of the two cylinders areintegrally secured together by suitable connections or joints 28 sothat, when one cylinder is rotated, the angular plunger structures willreciprocate in the bores of the cylinders and will also partake ofbodily movement and will transmit the rotation of the rotated cylinderto the other cylinder, all in a manner well unde'rstood in the art.

The outei' end of the cylinder 20 is closed by a wall 29 from whichextends axially a drive shaft 30, this shaft being j ournalled in thehead 15. The outer end of-the cylinder -22'i's closed by a wall 31 fromwhich extends axially a bearing stub 32 journalled in the head 17. Asupporting stud 33 extends from the head 17 by means of which the pumpstructure may e mounted on and secured to a support.

The end wall 29 of cylinder 20 has four ports 34 therethrough, one foreach of the bores 24, the ports being equidistant from the cylinder axisand spaced 90 apart. In the inner face of the head 15 are two arcuatechannels 35 and 36 extending concentric with the axis of the cylinderand adapted to register with the cylinder ports 34. These channels arenot quite semi-circular but their ends are separated by spaces 37 and 38whose width is equal to or slightly greater than the diameter of thecylinder ports 34. A passageway 39 through the head 15 connects thechannel 35 with one end of the passageway 40 through the longitudinallyextending boss 41 on the side of the housing 10, which pasthe outwardstroke of each plunger, the port will be in communication with theoutlet channel 36. At the end of each stroke of a plunger, itsassociated port will be closed by either of the faces 37 or 38 betweenthe ends of the channels. The plungers operate consecutively, and duringthe inward strokes, fluid will be drawn into the respective bores fromthe circuit connected with the channel 35, and during the outwardstrokes, such drawn-in fluid will be expelled through the outlet channel36 and to the fluid circuit connected with the outlet boss 44.

The end wall 31 of the cylinder 22 has two diametrically opposite portsa and b for the diametrically opposite plunger bores 26a and 26?), asshown in Figure 4. The wall 31 has also two other diametrically oppositeports 0 and d spaced 90 from the ports a and b, respectively, andcommunicating with the other pairs of diametrically opposite plungerbores 26c and 26d, as shown in Figure 3. In the inner face of the head17, there are diametrically opposite channels 45 and 46 for registeringwith the ports a and b, and concentric with such channels are the outerchannels 47 and 48 for registering with the ports 0-. and (Z as thecylinder 22 rotates.

The channels 45 and 46 are not quite semicircular but are separated attheir ends by spaces 49 and the ends of the channels 47 and 48a1'eseparated by spaces 50, the width of the faces being equal to orslightly greater than the diameter of the ports in the cylinder wall 31.

A passageway 51 through the head 17 connects the channel 45 with theinlet boss 52 on the head. A passageway 53 through the head connects thechannel 46 with the passageway 54 through the longitudinal boss 55 onthe side of the housing 11, this passageway communicating through a port56 with the chamber 19 at the juncture of the housings. A passageway 57through the head 17 connects the channel 47 with the outlet boss 58 onthe head and the passageway 59 through the head connects channel 48 withthe inlet boss 60 on the head.

With the arrangement above described in connection with the pump sectionB, the bores 26a and 26?) will communicate through the respective portsa and b first with the inlet channel 45 and then with the outlet channel46, so that during instroke of the plunger in each bore, the bore willbe filled with fluid which will be discharged during outstroke of theplunger, fluid drawn in through the boss 52 and passageway 51 being thuspumped through passageways 53 and 54 and port 56 into the chamber 19from where it is discharged through an outlet 61 from the chamber.

The plungers in the other bores 26c and 26d of the pump section B willdraw in fluid through the inlet boss and passageway 59 through port 0 orcl and will discharge it through the passageway 57 and the outlet boss58. There are thus two separate paths of fluid through the pump sectionB, the flow through one path being controlled by the plungers operatingin the bores 26a and 26b, and flow through the other path beingcontrolled by the operation of the plungers in the bores 260 and 26d.

In Figures 1 and 2 I have shown my improved pump structure in service ina system' for supplying combustion mixtures for an oil burner. Theangular pump structure is mounted and secured on a suitable base 62 bymeans of its lug 33. A motor 63, preferably electric, is mounted on thebase and by a suitable coupling 64 is connected with the drive shaft 30which extends from the cylinder 20 of the pump section A. i

An oil supply source 65 is also supported on the base 62, and thissource may be a wellknown type of vacuum tank ordinarily used on motorvehicles. I vacuum tank is connectedby a pipe 66 with an oil supplyreservoir (not shown) from which the oil is drawn by suction into thevacuum tank.. This suction is generated by the pump section B, a pipe 67extending from the top of the vacuum tank to the inlet boss 60 so thatthe operation of the plungers in the bores 260 and 2665 will pump airfrom the vacuum tank and discharge it through the outlet boss 58 andpipe 68 to an air ejector end or nozzle 69.

The oil, outlet of the vacuum tank is 'connected by apipe 70 with theinlet boss 52 in head 17 of the pump section B, so that the plungers inthe bores 26a, and 26b will operate to pump the oilfrom the vacuum tankand discharge it through the passage,- ways 53 and 54 and the port 56into the chain ber 19 from where it flows through the pipe 71 to theejecting end or nozzle 72. The oil flowing through the chamber 19 underpressure will act as a sealing medium for the plungers and cylinders andwill lubricate the bearing surfaces, and thepressure against the innerends of the cylinders will hold'them withtheir ported outer walls infirm seating engagement against the'inner faces of the respective pumpheads.

The flow of oil from the vacuum tank is preferably metered. In Figure 9,I show The upper part of the a practical form of adjustable meteringfitting interposed between the vacuum' tank and the pipe 70. Thisfitting comprises a body 73 having its inner end threaded through thebottom of the vacuum tank to communicate with the interiorthereof. Thebore 1'4 in the body 73 communicates with the passage 75 in the lateralextension 76 with which the pipe 70 is connected. Engaging in the innerend ofrthe bore 74 is a. metering pin 77 which has the longitudinalmetering port'78 of gradually increasing depth, so that, as the pin ismoved rela. tive to the inlet end of the bore 7 4, the available oilpassage area will be increased or d minished. A rod 79 extends from themete'ring pin through the bore 74 and throughthe plug 80 in which itterminates at its outerend in a head 81 provided with a screw-driverslot. The plug 80- is secured to the outer end of the body 73 and therod 79 has threaded engagement with the plug,

\ so that,when the rod is turned, the metering pin 7 7 will be shiftedaxially in the bore 74 to effect the proper fiow adjustment. Aprotection cap 82 is preferably applied to enclose the head of the rod,and this cap may thread onto the outer end of the plug 80.

The oil flow is further metered and limited by a fitting 83 in the formof a conduit interposed between the pipe 70 and the inlet boss 52 of thehead 17.' This conduit has the restricted metering outlet clearly shownin .Figure 4.

This carefully metered oil flow from the vacuum tank is supplied withair in metered quantities to be mixed therewith durport 84, as

ing flow through the pump section B. As

best. shown in Figure 6, the air intake tube 85 is connected with theinlet boss 52 of the pump head 17 by means of the elbow fitting 86. Theouter end 87 of the tube is exteriorly threaded and receives a can 88.The end87 has longitudinal grooves 89 forming air inlet passagewayscommunicating withthe atmosphere and with the interior of the cap 88. Ametering pin 90 is secured to the outer end of the cap 88 andextendsaxially in the end of thetube 85. This pin has a longitudinal channel 92whose cross sectional area gradually increases toward its outer end sothat asthepin is adiusted longitudinally when the threaded cap 88is-turned, the cross sectional area of thepassage 92 at the inlet end ofthe tube 85 determines the volume of air flow. Air enters the cap 88through the channels-89 in the threaded end 87 and from there flowsthrough the meter ng pin nassage 92 into the bore of the tube and theninto the boss 52 to mix with the-metered oil flow from the orifice 84,the air and oil durthe proper proportion of air and oil can be adjustedfor to a nicety. The flow of the oil through the restricted orifice 84under the suction of the pump causes the oil to be more or less brokenup and sprayed so that it will more thoroughly mix with the measured airdelivered thereto, the combined flow of oil and air through the pumppassageways, ports and bored together with the pump pressure, producinga very intimate mixture of the air and oil. This rich uniform combustionmixture is delivered by the pump section B through the passage 54 andport 56 into the chamber 19 and from there through the pipe 71 to theinjector end or nozzle 72, as best shown in Figure 8. This mixture,being delivered under pressure to the chamber 19, will be intimatelyapplied to the plunger and cylinder structures to thoroughly lubricatethese structures and to seal them against leakage. The pressure exertedagainst the cylinders will serve to hold them intimately and accuratelyagainst the faces of the respective pump section heads to thereby causeaccurate portage of the mixture through the pump and to prevent leakage.

As has already been explained, the plungers in the bores 26c and 261i ofthe pump section B serve to draw air through the vacuum tank and pump itto the ejector end or nozzle 69. This air is more or less laden withvapors and fumes of the oil flowing through the vacuum tank, andprovision is made to mix air from the atmosphere with such impregnatedair before it reaches the nozzle 69.

Referring to Figure 2, an air pipe 93 is con- (ill neeted with the inlet42 of the passageway 40 through the boss 41 on the pump housing 10.Referring to Figures 5 and 7, air is taken in through this path by thepump section A and delivered thereby under pressure through pipe 68 tothe pipe 68 by means of a fitting 94, so that this atmospheric air Willflow with the impregnated air to the ejector end 69,

- this atmospheric air flow being thus in parallel with the impregnatedair stream pumped by the pump section B.

The air supply pipe 93 has preferably a calibrated or restricted inletorifice 93 so that the air flow is metered.

Instead of connecting the air and oil supply terminals 69 and 72respectively directly with a burner or main injector nozzle, theseterminals preferably extend into closed chambers 95 and 96,respectively, as best shown in Figure 8. These air and oil chambers areprovided in a housing 97 which may be mounted on the support 62. The airsupply terminal 69 extends to an opening 98 at the bottom of the chamber95 which communicates with a downwardly tapering depression or pocket99. The oil terminal 72 extends to an opening 100 at the bottom of thechamber 96 which communicates with a downwardly tapering depression orpocket 101. These pockets 0r depressions may be formed in the support62. The pocket 99 -is connected by a pipe 102 with the inlet end of amain ejector or nozzle structure 103, whose outlet end 104 may beconnected to discharge directly into the firebox of a furnace or todischarge into a burner structure. The pocket 101 is connected by a pipe105 with a lateral induction inlet 106 on the main nozzle structure forconducting the oil stream into the path of the air flow through thenozzle structure so that during normal operation the oil will beinducted or drawn into the air stream, the combined air and oil beingthen 69 into the chamber 95 to build up pressure therein until suchpressure becomes sutficient to drive the air through the main nozzlestructure. Likewise, the oil delivered by the pump under pressure to theterminal 72 tends to flow through the pipe 105 to the main bore of themain nozzle structure, but, if the oil is not sufficiently rapidlyejected by'the main nozzle structure, the oil will back up in thechamber 96 until the orifice 108 is submerged and then the air above theoil will be compressed and the built up pressure will tend to force theoil through the main nozzle structure. Such building up of pressure inthe chambers serves several purposes. It maintains a more balanced andmore stable pressure of the air and oil flow to the main nozzlestructure, and prevents sudden fluctuation of the main nozzle dischargeand the combustion flame during otherwise disturbing condi tions. Forexample, in the case of sudden changeof draft in the firebox thebuilt-up reserve pressure in the chambers 95 and 96 will eflicientlydeliver the proper charge of air and oil through the main nozzlestructure so as to maintain the flame.

Another purpose served by the reserve back pressure built up in thechambers is to cause thorough cleansing of the oil path from theterminal 72 to and through the main nozzle structure, so that. after thesystem is closed down, there will be no dripping of oil from the nozzlestructure. As soon as the system is shut down and the pumps are stopped,the reserve back pressure in the chamber 95 will cause continued airflow through the main nozzle structure until the pressure in the chamberis relieved, and the accumulated pressure behind any oil which may beleft in the chamber 96 or in the pocket 101 will force this oil out andinto the path of the air flow through the nozzle structure so that suchsurlus oil will be delivered to the flame or the 'urner to be consumedafter the system has been shut down.

Briefly repeating the operation of the system, the plungers of the bores260 and 26d of the pump structure B serve to draw air from the vacuumtank and deliver it to the terminal 69, the suction effect generated inthe Vacuum tankbeing sufficient to maintain the necessary oil supplyflow through pipe 66 to the vacuum tank from the oil reservoir. To thisair supplied to the terminal 69 is added the atmospheric air pumpedby'all four plungers of the pump structure A, so that six plungers areeffective in pumping the air supply under pressure for the'main nozzlestructure.

The plungers in bores 26a and 26b of the pump section B pump from thevacuum tank, in measured quantity, the combustion oil to which air inaccurately metered quantities is added to be thoroughly mixed therewithbe fore reaching the terminal 72. I have found that by carefullymetering the oil flow and by metering and more or less restricting theair intake and supply, the operation of the pump will be much smootherand knocking or pounding will be prevented.

. While I have shown and described my invention in a preferred form,changes and modifications in the structure and arrangement may be madewithout departing from the spirit and scope of the invention, and Itherefore do not limit the invention'except as .specified inthe appendedclaims.

I claim as my invention: 1. In a combustion mixture supply system, thecombination of an angular rotary pump structure comprising two pumpsections havmg interconnected PlStOIlS, a combustion mixture deliveryelement, means for causing part of the pistons of one ofthe pumpsections to pump combustion fluid to said combustion delivery; element,and means for causing the other pistons of said pump section and all thepistons of the other pump section to pump air to said combustiondelivery element.

2. In a combustion mixture supply system, the combination of an angularrotary pump structure comprising two pump sections having interconnectedpistons, means for driving said structure, a source .of fuel supply, acombustion mixture delivery element, and means defining two separatepumping paths through'one of said pump sections, one of said paths beingconnected to pump fuel and the other being connected for the pumping ofair, the other pump section pumping air, the discharge ends of bothpumping sections being connected with said combustion mixture deliveryelement. e

3. In a combustion mixture supply system,

the combination of an angular rotary pump structure providing two pumpsections having interconnected pistons, a main source of fuel supply, anauxiliary source of fuel supply in the form ofa vacuum tank, deliverymeans for delivering combustion mixture, means providing two separatepumping paths through one of said pump sections, one of said paths beingconnected for the pumping of air from the vacuum tank for maintainingthe suction therein to replenish said tank from the. main source of fuelsupply, said other path being connected to pump fuel from said tank,said other pump structure being adapted to pump air, the discharge fromboth pump sections being received by said combustion delivery element.

4. In a combustion mixture supply system, the combination of an angularrotary pump structure providing two pump sections having interconnectedpistons, a main source of fuel supply, an intermediate source of fueling means for metering the oil flow through said fuel pumping path, ametered air supply inlet to said fuel pumping path, and means connectingsaid other pump sections for the pumping of air from the atmosphere, thedischarge outlets of said pump sections being connected with saidcombustion mixture delivery element. i

5. In a combustion mixture supply system,

the combination of an, angular rotary pump structure havinginterconnected pistons, a source of oil supply, a vacuum tank connectedwith said source, means causing part of said pistons to pump air fromthe atmos-' phere, means causing others of said pistons to pump air fromsaid tank for maintaining the vacuum therein, means causing theremaining pistons to pump oil from said tank, and means combining thepumped air and oil to form acombustion mixture.

6. In a combustion mixture supply system, the combination of an angularrotary pump structure comprising interconnected pumping elements, vacuumcontrolled fuel supply apparatus, means defining separate air pumpingpaths through said pump structure and an oil pumping path therethroughseparate from saidrair paths, said oil pumping path being connected toreceive 031 from said supply apparatus, one of said air pumping pathsbeing connected with said oil supply apparatus to furnish the vacuumtherefor, and means combining the pumped air and oil to form acombustion mixture.

7. In a combustion mixture supply system,

the combination of a pump structure providing an air pumping path and anoil pumping path, air and oil ejector members for the pumped air and oilrespectively, a combustion mixture delivery element having an airpassage and an oil intake communicating with said air passage, a closedchamber having an outlet connected with the air passage of the deliveryelement, said air ejector member extending into said chamber andterminating at its outlet, a second closed chamber having an outletconnected with the oil intake of said delivery element, said oil ejectorextending into said second chamber and terminating at its outlet, saidchambers serving to accumulate pressure caused by the resistance to theair oil flow through said delivery element and to apply said pressure tostabilfze the flow from said delivery element.

' 8. In a combustion mixture supply system the combination of acontainer divided into separate chambers, a pocket formed at the bottomof each chamber arranged for connection to an outlet conduit, an ejectormember secured in the top of each chamber having a lower end disposedadjacent to said pocket, one of said ejector members being for air andthe other for a combustible fluid, and a combustion mixture deliveryelement connected to the outlet conduits from said containers where theair and combustible fluid from the chambers are combined, saidcombustible fluid ejector being arranged so as to be sealed by theaccumulation of combustible fluid within its associated chamber.

9. In a combustion mixture supply system, the combination of an angularrotary'pump structure having two pumping sections, a housing for saidsections defining a mixing chamber at the junction of said sections,vacuum controlled fuel supply apparatus, means defining separateauxiliary air pumping, paths through said pump structure and a combinedoil and primary air pumping path separate from said auxiliary air paths,said oil and primary air pumping paths connected to receive oil fromsaid supply apparatus and primary air from atmosphere and deliver thesame to said chamber, one of said auxiliary air pumping paths beingconnected with a said oil supply apparatus to furnish the vacuumtherefor, and means combining the primary air and oil with the auxiliaryair to form a combustible mixture. 10. A combustion mixture supplysystem the combination of an angular rotary pump structure having twopumping sections, a housing for said sections defining a mixing chamberat the junction of said sections, reciprocable pumping elements in saidsections having their adjacent e'nds interconnected within said chamber,vacuum controlled fuel therefor, means causing other pump elements topump primary air from the atmosphere and oil from said supply apparatusand deliver the same to said mixing chamber, the

action of said elements in said chamber cans- In testimony whereof Ihave hereunto'subscribed my name at Chicago, Cook County, Illinois. y j

CHARLES L, RAYFIELD.

supply apparatus, means to cause partof said elements to pump auxiliaryair from said supply apparatus to furnish a vacuum 7

